Means for rolling disk wheels



Oct. F, 1929. J. W. SMITH 1,730,694

MEANS FOR ROLLING DISK WHEELS Filed.May 15, 1924 5 Sheets-Sheet l FIG.I-

WITNESSES.- v INVENTOR Jbhn W ,Smi W4,

A T QRNE YS.

Get. 8, 1929. J. w. SMITH 1,730,694

' MEANS FOR ROLLING DISK WHEELS 'Filed May 15, 1924 5 Sheets-Sheet 2 z12 fig W I TNESSE IN VE'N TOR I Lfohz p W Smiih {i TORNEYS 0d. 3, 1929.J. w. SMITH 1,730,694

MEANS FOR ROLLING DISK WHEELS Filed May 15, 1924 5 Sheets-Sheet 5 95JNVENTOR jbhn MK Smith,

BY v TORNEYS.

Oct. 8, 1929. J. .w. SMITH 1,730,594

MEANS FOR ROLLING DISK WHEELS Filed May 15, 1924 5 Sheets-Sheet 4 Hi7:M. Y

Illlllllll m WITNESSES: 11v VEN TOR w fi BY 06h msmzm, C? A (AW OwPatented Get. 8, 1929 JOHN V. SMITH, OF PHILADELPHIA, PENNSYLVANIA MEANSFOR RQLLING- DISK 'VVHEELS Application filed May 15,

This invention relates to a novel manner of rolling disk wheels forvehicles such as automobiles and the like, and also to means useful tothis end.

The primary object of my invention is to produce from a roughly preparedblank, an extremely light and strong disk wheel characterized by anintegral hub, a dished cross section for sturdiness against lateralthrust,

and radial tapering of the metal to a degree of fineness hithertoimpossible of attainment.

Attempts have been made to produce a disk wheel having the attributesoutlined by drop-hammer forging, or the use of hydraulic presses andbulldozers, but it has proved absolutely impossible to obtain a crosssection of suitable thinness to meet the critical requirementsassociated with a light wheel for automobile use, on account of theinherent g molecular resistanceof metal to flow in a clirection at rightangles to that of applied force. To overcome the disadvantage referredto, and according to my invention, I employ narrow faced rollers mountedwith capacity for cycloidal oscillation by a novel form. of mechanism.

Subsidiary objects and advantages, will be apparent from the followingdescription of a typical embodiment of my invention, the appended claimsserving to indicate the features which I believe to be novel andpatentable.

In. the drawings, Fig. I is a side elevation, showing a mill adapted forthe rolling of disk wheels in accordance with this invention, certainportions being, however, broken away to disclose underlying features.

Fig. II is a longitudinal section of the greater portion of the mill ona somewhat enlarged scale.

Fig. III is a transverse vertical view taken as indicated by the arrowsIII-III in Figs. I and II.

Fig. IV is a diagrammatic sectional View taken approximately on a planeas indicated by the arrows IV-IV in Fig. I, to show a controllingmechanism for the mill rollers, as well as means for intermittentlyprogressing a turret whereby the blanks are successively presented forrolling.

Fig. V is a transverse sectional View taken 192%. Serial No. 713,425.

is had to Figs. VII and VIII wherein the numeral 1 indicates the formingdie, and 2, cooperating rollers whereof there may be several, two being,however, deemed ordinarily sufficient. The face of t-hcdie 1 is given,what I preferably term, an woo repl ca cross sectional profile thatdetermines the general configuration of the finished article. Use of theterm arcographic, hereinafter, is intended to broadly apply to asectional profile of a curvature not struck from a common center butrather of gradual deviation therefrom. I11 the manufacture of diskwheels for vehicles, the die-face is formed with a cycloidal concavity 3that is symmetrical relative to the vertical axis about which the die 1is rotated. The rough blank wherefrom the disk wheel is fashioned andshown at B in Fig. VII, may be produced by drop forging from an ingot ofpredetermined size and bulk, with a circular disk portion and anintegral frustoconical axial boss H, which is ultimately to becomethe'wheel hub. The discous portion of the blank B-shown as an exampleonlytapers in cross section at the region of its mergence a with the hubbossH, and also at the region of its periphery b. The bore of the boss His coned inwardly from the opposite ends 0, d to facilitate support onthe one hand by a stud 4, which, together with others is mounted. on afeeding means to be hereinafter described, and onthe other hand, by acentering pin 5 located medially of the die 1. When the blankB isproperly positioned, the tapered hub-boss H is accommodated with a firmand snug fit in a correspondingly-tapered portion 6 of the die-boreunder upward pressure maintained on the stud as hereinafter noted, toprevent relative movement between the blank B and the die 1 duringrolling. Upon placement of the blank B as just explained, the rollers 2are simultaneously elevated under pressure exerter from beneath, fromthe iulldine to the dotted line position in Fig. VII, with the resultthe discous yields to upward bending during the first pass of therollers 2. After aslight pause in the initial attack the rollers 2 aremoved outward and at the same time swung bodily upon centers determininga curvilinear course substantially in parallelism to the cycloidalconcavity 3 on the die face. As a consequence, the metal of the blank Bis urged forward by the rollers 2, determining radial flow which isattended both by radial and compensative circumferential expansion ofsaid blank, brought about by the narrow faced rollers 2 rotating uponthe metal in a cycloidal direction. To attain this end. the rollers 2are mounted in trunnions with capacity for adjusting their movement ofdeviation relative to the center of the cycloidal concavity 3. andthereby control the ratio of metal thickness at the hub zone and outerperiphery of the disk.

By proper determination of the axis about which the rollers 2 areoscillated. I am en abled to obtain an attenuated cross section that ishighly desirable in disk wheels for automobiles. Thusby respectivelyswinging the rollers 2 bodily on acenter slightly eccentric to that ofthe die curvature. I obtain the outwardly attentuated cross sectionalconfiguration of blank shown in dotted lines in Fig. VII. and in fulllines in VIII. A greater degree of thinness with correspond ing radialand circumferential expansion of the blank B may be hat by a second passof the rollers 2, but with said rollers operating progressively closerto the die 1. The result of a second pass. carried out as suggested. isshown in dotted lines in Fig. VIII, the difference being made apparentby contrastwith the full line cross section obtained by the initialrolling. In practicel have tound that the operation of rolling inaccordance with my invention may be accomplished with the utmost casewhen the blank is preheated, the metal flowing without any tendencywhatever to buckle or fracture. Furthermore, by using rollers 2 withcomparatively narrow spherical treads 7, as herein shown, the first passmay be completed without any appreciable temperature drop in the blankB, so that the second pass can be accomplished under the same favorableconditions without necessity for reheating the blank. With the mill nowto be described it is possible to completely roll a wheel by two passesin approximately eighteen seconds, and even in less time.

Referring genoraly to Figs. I to V oi the drawings, it will be seen thatthe forging die 1. is rotatably held in suspension by a hollow head 10,supported by tubular columns above a base 12. This head 10 is recg'ularin plan and formed with integral 1. o sting corner bosses l3 bored tolit the upper reduced ends oil the columns 11, as shown in s ction inFig. I. To permit slight vertical adjustment of the head 10, I provilecollars let that engage threaded portions 15 of the columns 11;companion collars 16 in similar engagement with the upper ends of rods1? extending axially through said ans ll, serving to fix the position ofthe head 10 after the desired adjustmentis made. T's shown bestadvantage in Fig. II, e die is bolted to the lower circumferentiallyextended port-ion 18 of a cl member 19 journaled centrally in the 10with anti-"friction roller bearings The swivel ular ledge 22 formed inthe base of a contop cavity 23 of said head. The upward imparted to thedie 1 during the g peration is resisted by a thrust bearing 2i which isdesigned to insure absolute freedom of motion and amply proportioned tovithstand the heavy strains that itis subiected to. The bearing 21% isaccommoled within a lower hollow 25 01 the head 10 set apart by ahorizontal diaphragm 26. The circumferential portion 18 ot the swivelmember 19 has an integral upstanding pcripheral flange 27 that extendsinto the lower cavity 25 and provides an oil well for imincrrlon or" thethrust bearing 24:, the top edge oi said flange being turned outwardlyand downwardly to overlap an annular vertical. age 28 of a cover plate29 closing the cavity As a means for driving the swivel member 19 I mayemploy any convenient type of prime mover, for example an electric motorrepresented conventionally by the dotted lines 30 in Fig. II, and shownas supported upon the top of the head 10 across its upper center cavity23. The shaft of the motor 30 carries a clutch collar 31 designed toengage directly with the cap piece 21 crowning the swivel member 19,said cap piece being formed with vertically projecting lugs 32 for thispurpose.

The centering pin 5, previously referred to, is secured to the lower endof a plunger independently rotatable and free to reciprocate in a guidehousing 34 accommodated with circumferential clearance in the hollow. ofthe swivel member 19. A helical spring surrounding the reduced portion.of the plunger 33 and engaging the shoulder aii orded by its broaderbottom end. serves to urge the pin 5 downward or outward through the die1, the limit of such motion being determined by a stop plate 36 thatslightly over.

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laps the open end of the guide housing 34 and intercepts acircumferential protuberance 37 of the plunger 33.

In order to insure proper lubrication of the various bearings associatedwith the head 10, and at the same time to dissipate the heat transmittedto them by conduction from the die 1, I maintain a constant circulationof a suitable lubricating medium through the head. The lubricant entersthe head 10 by Way of apipe 38 that leads directly to an internal groove39 surrounding the swivel member 19 immediately above the roller bearing20. A portion of this supply passes through openings 40 in the headstructure, said openings leading to the bearing surface 22 for the cappiece 21. In passing through the bearing just described, the oil entersthe central upper cavity 23 of the head 10 and accumulates to the levelshown, determined by the height of the over-flow outlet 42 which leadsdownwardly and discharges into the well 27 formed about the thrustbearing 24 as previously described, to lubricate said hearing. A portionof the lubricant also passes from the internal groove 39, through radialports 43 of the swivel member 19, and enters the clearance space aboutthe housing 3 1 for the centering pin plunger 33. After cooling theparts in this vicinity, the lubricant continues its coursethrough ports1 1 in the lower portion of the swivel member 19 finding its way into anannular chamber 45 about saidmember to assist in the lubrication andcooling of the thrust bearing 24:. The overflow from the well 27 aboutthe thrust bearing 24: discharges into the lower cavity 25 of the head10 wherefrom it is conducted through a return pipe 46. A conventionalcooling devicenot shownmay be connected in the circuit of the pipes3841-6.

As will be observed from Fig. II, the rollers 2 have shafts 50, hereshown integral but they may be detachablethat are mounted in individualtrunnion housings 51. Each housing 51 is formed with an integral yoke 52from the ends of which project outwardly in respectively oppositedirections, polygonal. lugs 53 that provide, in conjunction withseparable collars 54: thereon, the trunnions about which the housingswings to effect radial movement of the corresponding roller 2 relativeto the die 1 for determining the desired cycloidal movement of theroller tread 7. The trunnions for each of the roller housings 51arereceived in bearings 55 of a trunnion support 56 provided with slidableguides 57 mounted upon the columns 11 in moving the rollers 2 verticallytoward and away from the die 1. By reference to Fig. III of thedrawings, it will be seen that the shifting of the trunnion support 56is controlled by aid of toggle links 58 of which there are four sets toinsure absolute accuracy of the trunnion support movements. One link ofeach pair is while the other is connected to the base 12,

i the common pivotal centers 59 of each transversely aligned pair of thetoggles being joined by a link 60 for the purpose of simultaneousoperation. The lower links of the pair of toggles at the lefthand sideof the mill, as considered in Figs. III and V, are coupled by connectingbars 61 with rocker arms 62 that are secured to a shaft 63 extendinglongitudinally of said mill, (see Fig. I) and journaled in bearingbrackets 64, 65 rising from the base 12. The rock shaft 63 receivesmotion, through the instrumentality of a second arm 66 secured theretoat its left hand end (Fig. I), said arm carrying a roller 67 which ridesagainst the edge of a rotary cam 68 fixed upon the main shaft 69, fromwhich the various mechanisms of the mill derive their motion. As shownin Fig. V, the rotary cam 68comprises two segmental rises 70, 71

which differ in radial depth soas to determine, during rotation of saidcam in the direction of the arrow thereon, the proper successivepositions of the rollers 2 relative to the die 1, as required for thetwo passes of the complete operation, the position of the toggles 58 forthe first pass being indicated by dot-and-dash center lines in thereferred to illustration. As a means for tripping the toggles 58 for thetrunnion support 56, an associate cam 72 is secured to the main driveshaft 69 adjacent the rotary cam 68, said associate cam having tripprojections 73, 7 4 that successively engage a roller arm 75 fixed tothe shaft 63 with the arms 62, 66, previously referred to. Thus, afterthe completion of eachpass, the rocker shaft 63 is actuated to upsetthetoggle setting to permit lowering of the trunnion support 56 andreturn of the rollers 2 to their normal lowered position, retracted fromthe die 1.. i

Referring again to Fig. II, it will be noticed that a roller bearing 76is in each instance provided to take the mam strain adjacent the roller2, while an additional ball bearing" 77 sustains the shaft 50 at theopposite eX- tremityf The trunnion housings 51 are closed.

in at their outer ends by covers 7 8,. bolts 79 being employed to urgethe annular flange 80 against the outer ring of the ball bearings 77,and retain the same in place. The trunnion roller housings 51, as wellas the bearings 76, 7 7 for the roller shaft 50, are cooled andlubricated by oil introduced in each instance through a pipe 81 thatenters the polygonal lug 53 at the side of the mill shown in Figsbearings to the chamber within the cover member 78. After havingperformed the function of lubricating the bearings 76, 77, the oilpasses through ports in a plate 84 that covers an axial passage 85through the shaft 50, and in order to effectively cool the latter, isobliged to traverse the full length of the same before escaping, throughports 86 of a plug 87 at the roller end of said shaft, into a tube 88which extends through the axial passage 85. This tube 88 leads to therear end of the trunnion housing 51 from which the oil is drawn througha pipe 89 fitted into the cover member 78. The pipe 89 just referred to,is made of flexible material so as to enable swinging of the trunnionhousing 51 during the rolling operation, and any appropriate means maybe employed to induce circulation of the lubricant through the deviouspassages in said housing.

Slight adjustment of the rollers 2, may be had by the means best shownin Figs. II, III and VI, where it will be noted that the polygonal lugor trunnion 53, fits a correspondingly shaped, though wider. opening 90in the sleeve 54. Replaceable interchangeable shims 91 are insertedbetween the polygonal lug 53 and one side of the opening 90, as shown,and set screws 92 taking into the sleeve 54, press said lugs ortrunnions firmly against the shims 91 to hold the several parts in rigidassemblage. WVear of the roller treads 7 may be compensated for, fromtime to time, by interchanging the shims 91, as will be readilyapparent. A further adjustment is afforded the rollers 2 by the use of abearing lining 93 with an eccentric bore 94 to take the separable collar54. From the lining 93 projects radially at the exterior of the bearing55, a lug 95 having associated therewith a bolt 96 which may be engagedwithin any one of a number of openings 97 in the face of the hearing 55,to secure said lining in adjusted positions. This adjustment permitscorrection of the center of oscillation of the trunnion housing 51, withcorresponding change in the relation of the tread of the roller 2 to thecycloidal concavity 3 in the die 1 and alteration of the thickness towhich the blank is rolled. Still another adjustment for each of therollers 2,in an axial direction-may be had by the use of interchangeableshims 98 between the ball bearing 77, and the annular seat 99 therefor,at the interior of the trunnion housing 51.

The mechanism for oscillating the housings 51 about their trunnion axes,includes a rotary master cam 100, see Figs. I and IV, aflixed to themain drive shaft 69 at the right of the rotary cam 68 aforementioned.This master cam 100 has two rises 101, 102 which, function successivelyduring the two passes of the rollers 2 in rolling the blank B. The camrises 101, 102 of the master cam 100, affect a roller arm 103 on ahollow rocker shaft 104, located above, and extending in.

parallelism to the rocker shaft 63 previously described. The shaft 104is journaled in bearings 105, 106 and adjacent these bearings hasdepending arms 107, 108 connected by links 109 with motion translatingmembers 110, pivoted upon the opposite ends of an axle shaft 111,extending longitudinally through the trunnion support 56. The translating arms 110 are pitched angularly as illustrated in Figs. I and II,and are in turn coupled by links 112 respectively, with studs 113projecting laterally from the trunnion housings 51 for the rollers 2,universal fittings 114 being employed in attachment of the links 112 topermit the freedom required for their complex movement. Thus, as themaster cam 100 is rotated in the direction of the arrow in Fig. IV, itwill be apparent that the trunnion housing-s 51 will be oscillated onthe bearings 55 in guiding the rollers 2 to cycloidal movement radiallyof the die 1, as already understood. The action of the master cam 100 isrendered absolutely positive, by an adj acently disposed follower cam115, (Fig IV), provided with two rises 116, 117 and functional to impartmovement to a roller arm 118 clamped on the rocker shaft 104. A study ofthe illustration last referred to, will reveal the fact that thefollower cam serves to maintain the roller on the arm 103 constantly inoperative engagement with the master cam 100.

For automatically feeding the blanks B successively into posit-ionrelative to the die 1 for rolling, and at the same time removing therolled wheels from the mill, I have devised mechanism as follows:Mounted to the trunnion support 56 with capacity for independent slidingmovement, is a saddle member 120 that carries a depending cylindricallug 121, guided for vertical movement in a central boss 122 of saidsupport, see Figs. II and III. The lug 121 is made hollow to house ahelical spring 123 which seats in a recess 124 formed in the bottom web125 of the support 56. As will be best understood from Fig. III, thespring 123 urges the saddle member 120 upwardly relative .to thetrunnion support 56, motion being limited by a collar 126 applied to thelower end of the lug 121 and adapted to engage the contiguous end of theboss 122. The saddle member 120 serves to support for free rotation, aturret feed in the form of an annulus 127 comprising two complementalhalves split at diametrically opposite points for ease in application tosaid saddle member, and these halves are clamped together by bolts 128.This annulus 127 carries the studs 4, which, as previously eX- plained,support the blank Ii during the rolling operation. The inner peripheryof the annulus 127 has notches 129 adapted to be pawled by a pin 130extending cross-wise between the ends of the parallel bars of a link 131that is connected at its opposite extremity,

mamma l with capacity for adjustment, to an arm 132 fast upon the rockshaft 104 intermediate the arms 107, 108 so as to be operable under theinfluence of the master cam 100 and its associated follower cam 115.During each rotation of these cams 100, 115, the link 131 carrying thepawling pin 130 is reciprocated twice,- but owing to the configurationof the follower cam 115 at the region 115, only one of these movementsis sufiicient to effect complete retraction of the pin 130 to engage ina succeeding notch 129 so that the annulus 127 is shifted but once foreach cycle of operation. The result of the shifting of the annulus 127is to bring a fresh blank B into position beneath the die 1, while thepreviously finished wheel disk is simultaneously conducted to a chute134 shown in Fig. III for discharge from the apparatus, the chute 134automatically stripping said previously finished disk from thesupporting stud 4 during movement of the turret annulus 127. It is, ofcourse to be understood that the shifting of the annulus 127 occurs whenthe trunnion support 56 is in its lowered position; and that while saidsupport is being raised, to position the blank relative to the die 1 forrolling, the saddle member 120 yields under the cushionf ing action ofthe spring 123. When the trunnion support 56 is fully elevated thespring 123 functions to maintain the blank B firmly pressed against thedie 1, and holds it securely against displacement during rolling.

To render the studs 4 free for rotation in synchronism with movement ofthe die 1, they are mounted in replaceable bearing sleeves 135 screwedinto cavities 136 in the periphery of the annulus 127, shoulders 137 atthe inner ends of said studs insuring their retainment. In each instancea ball bearing 138 is also utilized to take the vertical thrust of thestud 4.

Any suitable means may be employed for imparting rotary motion to themain shaft 69; for example a worm gear couple may be conveniently used,the same being concealed in the present instance within a protectivecasing shown at 140 in Figure I of the drawings, with a horizontal shaft141 extending through said casing for power application.

The operation of the mill is as follows The blanks B are successivelyplaced by the operative upon the studs 4 at the right hand side of themill as considered in Figure III. When the trunnion support 56 is in itslowered position, the turret annulus 127 is shifted to advance the blankB beneath the die 1 in axial ali nment therewith, actuation of saidannulus being effected by movement of the master and follower cams 100,115 through the various interposed connections coupled with them. As thetrunnion support 56 is elevated by movement of the toggles 58 to thedot-and-dash or first pass position of Fig. V, through action of therise of rotary cam 68 on the main shaft 69, the blank B is brought intodirect contact with the cycloidal concavity 3 in the die 1 by raising ofthe saddle member 120 upon which the turret annulus 127 is mounted. Theapproach of the blank B to the die 1 is facilitated by engagement of thecentering pin 5 within the tapered bore of the hub boss I-I, said pin 5incidentally receding automatically with the spring 35, to which it issubject. lVhen once properly positioned, the blank B is maintained infirm contact with the die 1 during the rolling operation by compressiveaction of the spring 123 which urges the saddle memher 120 upwardly.Concurrently with the elevation of the trunnion support 56, the rollers2 are brought into contact with the blank B in readiness to roll thesame, whereupon they are simultaneously swung outwardly in a directionradially of the die 1 by oscillation of their trunnion housings 51,which operation is brought about through the action of the first passrise 101 of the master cam 100, upon the roller arm 103 and associatedparts. Immediately upon completion of the outward sweep of the rollers2, the support 56 is lowered, and the arm 103 incidentally permitted toreturn to the position shown Fig. IV to restore said rollers 2 to thenormal position shown in full lines throughout the drawings. In likemanner the second pass of the rollers 2 is effected through a secondupward movement of the v trunnion support 56 and oscillation of thehousings 51 in the order mentioned. Upon completion of the two passes,whereby the blank is completely rolled in accordance with my invention,and the final lowering of the trunnion support 56, the turret annulus127 is again shifted to present a new blank B to the die 1, and at thesame time to automatically discharge the blank previously rolled on tothe chute 134, for removal from the mill.

While I have shown and describedmy in vention in connection with themanufacture of automobile wheels, it is obvious that the same may beemployed for production of other articles in which a dished sectionalprofile and tapering of the metal are required. It is also to beunderstood that while it is advantageous in rolling wheels in accordancewith my invention to effect the operation by two (or more) passes of therollers 2, there are instances where the operation can be accomplishedby a single pass as in rolling heavier wheelsnot requiring such a highdegree of attenuation. Itis also pointed out that a mill such as hereindescribed may also be employed to advantage in smoothing, shaping, andfinishing a wheel otherwise fully formed.

Having thus described my invention, I claim 1. A rolling mill comprisingan arcographic die, a cooperating rolling means, and means prescribingmovement of the rolling means to fashion a metallic blank of attenuatedcross section by outward expansion.

2. A rolling mill comprising an arcographic die, a cooperating rollingmeans, and means prescribing movement of the rolling means to fashion ametallic blank by outward expansion into conformity with the die, andconcurrently define linear expansion of the blank to an outwardlytapering cross section.

3. A rolling mill comprising an arcographic die, cooperating rollingmeans, and means prescribing curvilinear movement of the rolling meansto reduce a metallic blank by outward expansion into conformity with thedie and concurrently effect diametric expansion of the blank to definean outwardly tapered cross section therefor.

4. A rolling mill comprising an arcographic die, a cooperating rollercapable of eye oidal movement to fashion a metallic blank by outwardexpansion into conformity with the die and concurrently effect formationof said blank to tapered cross section, and means whereby the path ofthe roller movement is altered to vary the degree of taper.

A rolling mill comprising an areagrapl'iic die, anu a cooperating rollercapable of curvilinear movement about a point eccentric to the center ofthe die curvature in fashioning a metallic blank by outward expansion toconform thereto and simultaneously effect formation of the blank tooutwardly tapered cross section.

6. A rolling mill comprising an arcographic die, a cooperating rollercapable of curvilinear movement about a point eccentric to the center ofthe die in fashioning a flat metallic blank to conform thereto andconcurrently effect expansion of said blank to tapered cross section,and means whereby the eccentric movement is varied to alter thecross-sectional taper.

7. A rolling mill comprising an arcograplr ic die, and a cooperatingroller capable of eccentric curvilinear movement relative thereto ineffecting outward expansion of a metallic blank, said roller having acomparatively narrow tread for minimum surface contact to permitsuccessive rollings without requiring reheating of the blank.

8. A rolling mill comprising an arcographic die, a cooperating roller,means for curvilinearly guiding the roller in a gradually advancingdirection radially outward from the center of the die, and means forwithdrawing the roller at the end of its outward pass and restoring thesame to position for effecting successive passes.

9. A rolling mill comprising an arcographic die, a cooperating roller,means for cycloidally guiding the roller to follow substantially theconfiguration of the die with a graduated approach, means to determinesuccessive passes of the roller, and means concurroller including arotary cam, and motion transmitting means interposed between the cam andthe roller mounting.

12. A rolling mill comprising an areagraphic die, a cooperating roller,a mounting whereon the roller is bodily swung to follow the diecurvature, means for oscillating the roller for consecutive passesincluding a rotary cam with a succession of radial rises, and interposedmeans for imparting the motion of said cam to the roller mounting.

13. A rolling mill comprising an arcographic die, a cooperating roller,a mounting whereon the roller is bodily swung to follow the diecurvature, a rotary master cam foroscillatin the roller and actuatingthe rocker arm, a follower cam associated with the inaster caminfluential upon a second rocker arm to maintain the same at all timesin operative contact with said master cam, and interposed means wherebythe movement of said rocker arms imparted to the roller mounting.

14. A rolling mill comprising an emograpl ic die, a cooperating roller,an elongated journal housing for the shaft of said roller, a trunnionmounting for the journal housing whereon the roller is bodily oscillatedto follow the die curvature, and means determining circulation. oflubricant through the trunnion mounting and back and forth in the rollerjournal housing to lubricate and cool the various bearings associatedtherewith.

15. A rolling mill comprising an arcographically concaved d e, acooperating roller effective to outwardly expand a blank being rolled, amounting whereon the roller is oscillated to follow the die curvature infashioning said blank to conform to the die, and means for shifting themounting to move said roller toward and away from the die.

16. A rolling mill comprising an arcographically concaved die, acooperating roller, a mounting whereon the roller is oscillated todi'h'fcrentially follow the die curvature outwards in fashioning a blankto taper cross section, and toggle links operative upon the mounting tomaintain the roller in pressure contact with the'blank.

17. A rolling mill comprising an arcographically concaved die, acooperating roller, a mounting whereon the roller is oscillated tofollow the die curvature, toggle links operative upon the mounting tomaintain the roller in pressure relation with the die, and meanscontrolling the toggles to sue cessively position the mounting closer tothe die concurrently with successive passes of the roller.

18. A rolling mill comprising an arcographically concaved die, a supportfor the blank to be formed movable toward and away from the die, andmeans operative upon the support whereby the blank is maintainedyieldingly in contact with the die.

19. A rolling mill comprising an arcographic die, a support for theblank to be rolled, a carriage for the support movable toward and awayfrom the die, and a spring means interposed between the support and itscarriage to maintain the blank in contact with the die.

20. A rolling mill comprising a die, a turret for moving blanks to berolled successively into position relative to the die, a carriagesupport for the turret, means for shifting the carriage to advance theblanks into engagement with the die upon successive presentation, andmeans for intermittently rotating the turret when the carriage is inretracted position.

21. A rolling mill comprising a rotating die, a turret feed carrying asuccession of freely revolvable studs for individual mounting ofcentrally apertured blanks to be rolled, a carriage support for theturret, means for shifting the carriage to advance the blanks intoengagement with the die, and means for intermittently rotating theturret when the carriage is retracted to advance the blanks successivelyinto aligned position relative to the die.

22. A rolling mill comprising a die, a support from which the die issuspended for free rotation, a roller cooperating with the face of thedie, means for exerting upward pressure to urge the roller toward thedie in fashioning a heated blank into conformity therewith, and meansfor circulating lubricant through the support to cool the bearings andassociated parts against heat conduction.

23. A rolling mill comprising a rotating die, an electric motorconnected by a suitable coupling for driving said die, milling rollersfor reducing a metallic blank to the required thickness by expanding itsdiameter and face. and means for feeding successive blanks through themill.

In testimony whereof, I have hereunto signed my name at Philadelphia,Pennsylvania, this 12th day of May, 1924.

JOHN W. SMITH.

pressure

